CN202451425U - Compressor - Google Patents
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- CN202451425U CN202451425U CN2012200277608U CN201220027760U CN202451425U CN 202451425 U CN202451425 U CN 202451425U CN 2012200277608 U CN2012200277608 U CN 2012200277608U CN 201220027760 U CN201220027760 U CN 201220027760U CN 202451425 U CN202451425 U CN 202451425U
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- mentioned
- compression unit
- iron core
- rotor
- compressor
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- 230000006835 compression Effects 0.000 claims abstract description 68
- 238000007906 compression Methods 0.000 claims abstract description 68
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical group [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 claims abstract description 45
- 239000003507 refrigerant Substances 0.000 claims description 29
- 238000004804 winding Methods 0.000 claims description 3
- 230000002093 peripheral effect Effects 0.000 abstract description 3
- 239000003921 oil Substances 0.000 description 20
- 238000010586 diagram Methods 0.000 description 7
- 238000007599 discharging Methods 0.000 description 5
- 229910000831 Steel Inorganic materials 0.000 description 2
- 229910052742 iron Inorganic materials 0.000 description 2
- 239000010959 steel Substances 0.000 description 2
- 238000003756 stirring Methods 0.000 description 2
- 240000001973 Ficus microcarpa Species 0.000 description 1
- 238000004378 air conditioning Methods 0.000 description 1
- 230000004323 axial length Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000008602 contraction Effects 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 239000000314 lubricant Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 238000004904 shortening Methods 0.000 description 1
- 239000006200 vaporizer Substances 0.000 description 1
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- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The utility model provides a compressor capable of reducing oil feeding in a small-sized and high-capacity compressor. The axial thickness of a rotor iron core (31) and the delivery volume (CR) of a compression unit (2) meet the relationship that T/CR is less than or equal to 2.5. A first balancing weight is configured not to be intersected with a straight line (L) connecting the radial inside part (P1) of the inner edge of an exhaust port (340a) and the peripheral end edge (P2) of the rotor iron core (31) when a rotor (30) rotates.
Description
Technical field
The utility model relates to the compressor that for example in air-conditioning or refrigerated warehouse etc., uses.
Background technique
In the past; Have following compressor, this compressor has: seal container, be configured in the compression unit in the above-mentioned seal container and be configured in the above-mentioned seal container and the motor that drives above-mentioned compression unit via axle (with reference to No. 4168506 communique of japanese: patent documentation 1).
Above-mentioned axle has the exhaust port that is used for the oil that the oil storage tank from the bottom drinks up is delivered to periphery, so that be blown out to outside fluid from this exhaust port the mode of colliding takes place, and is provided with balancer weight at the rotor iron core of above-mentioned motor.
But, in above-mentioned existing compressor, be discharged to outside refrigerant gas from above-mentioned compression unit and also possibly collide with balancer weight.That is, the refrigerant gas of discharging from compression unit from compression unit when the rotor of motor and the air gap between the stator flow, balancer weight hinders flowing of refrigerant gas.Thus, the flow velocity of refrigerant gas is local to be increased, and the oil of bottom oil storage tank is swarmed, and exists oil to be brought to the outer problem of compressor (below be called oil (Ga り on the oil)).
Recently, require size little and have a compressor of big compressed capability.In this compressor, reduce compressor size through the thickness that reduces rotor iron core, still, when reducing the thickness of rotor iron core, the axial length of the air gap between rotor and the stator shortens, and oil separates path contraction.On the other hand, increase compressed capability through the discharge volume that increases compression unit, still, when increasing the discharge volume of compression unit, the flow velocity of the refrigerant gas of discharging from compression unit increases.
Like this, in the compressor of small-sized and big ability,, there is the tendency that oils and further increase because oil separates the shortening in path and the increase of refrigerant gas flow velocity.
No. 4168506 communique of [patent documentation 1] japanese
The model utility content
Therefore, the problem of the utility model is, provides and can in the compressor of small-sized and big ability, reduce the compressor that oils.
In order to solve above-mentioned problem, the compressor of the utility model is characterised in that this compressor has: seal container; Compression unit, it is configured in the above-mentioned seal container; And motor; It is configured in the above-mentioned seal container; And drive above-mentioned compression unit via axle, the stator of above-mentioned motor is disposed at the radial outside of the rotor of above-mentioned motor across air gap, and the coil of said stator is wound in the stator iron core of said stator; Above-mentioned coil is the concentrated winding that is wound in each tooth portion; Rather than a plurality of tooth portion of crossing over the said stator iron core reels, and the discharge volume CR of the axial thickness T of the rotor iron core of above-mentioned rotor and above-mentioned compression unit satisfies the relation of T/CR≤2.5, and above-mentioned compression unit has exhaust port with the opposed side of above-mentioned rotor iron core; Refrigerant gas after this exhaust port will be compressed in above-mentioned compression unit is discharged to outside the above-mentioned compression unit; Radially inner side in the inner edge of above-mentioned exhaust port partly is positioned at the side near above-mentioned axle, in the plane that comprises the said radially inner side part and the axis of above-mentioned axle, when partly periphery ora terminalis of the approaching above-mentioned radially inner side that utilizes straight line to connect above-mentioned radially inner side part and above-mentioned rotor iron core; Balancer weight in the end face setting of leaning on above-mentioned compression unit side of above-mentioned rotor iron core is configured to, and when above-mentioned rotor rotation, does not intersect with above-mentioned straight line.
Compressor according to this model utility; The discharge volume CR of the axial thickness T of above-mentioned rotor iron core and above-mentioned compression unit satisfies the relation of T/CR≤2.5; So; Can reduce compressor size through the thickness that reduces rotor iron core, and, can increase compressed capability through the discharge volume that increases compression unit.
And above-mentioned balancer weight is configured to, when rotor rotates; Do not intersect with the straight line of the exhaust port that is connected compression unit with the periphery ora terminalis of rotor iron core; So, refrigerant gas from exhaust port when air gap flows, balancer weight can not hinder flowing of refrigerant gas.Thus, the flow velocity of refrigerant gas can not increase, and can reduce oiling.
Therefore, little and have in the compressor of big compressed capability in size, can reduce oiling.
And in the compressor of a mode of execution, above-mentioned compression unit has: the 1st cylinder, and it has the 1st cylinder chamber; And the 2nd cylinder, it has the 2nd cylinder chamber.
According to the compressor of this mode of execution, above-mentioned compression unit is the two cylinders with the 1st cylinder and the 2nd cylinder, so, can further increase the discharge volume of compression unit, further increase compressed capability.
Compressor according to this model utility; The discharge volume CR of the axial thickness T of the rotor iron core of above-mentioned rotor and above-mentioned compression unit satisfies the relation of T/CR≤2.5, and above-mentioned balancer weight is configured to, when rotor iron core rotates; Do not intersect with the straight line of the exhaust port that is connected compression unit with the periphery ora terminalis of rotor iron core; So, little and have in the compressor of big compressed capability in size, can reduce oiling.
Description of drawings
Fig. 1 is the sectional view of a mode of execution that the compressor of the utility model is shown.
Fig. 2 is the planimetric map of motor.
Fig. 3 is the enlarged view of compression unit.
Fig. 4 is the major component enlarged view of compressor.
Fig. 5 illustrates the height of balancer weight and the diagram of the relation of the rate that oils.
Embodiment
Below, specify the utility model according to illustrated mode of execution.
Fig. 1 illustrates the sectional view of a mode of execution of the compressor of the utility model.As shown in Figure 1, this compressor has: seal container 1; Compression unit 2, it is configured in this seal container 1; And motor 3, it is configured in the above-mentioned seal container 1, and drives above-mentioned compression unit 2 via axle 12.This compressor is the rotary compressor of high-pressure dome type, in above-mentioned seal container 1, above-mentioned compression unit 2 is configured in the below, and above-mentioned motor 3 is configured in the top.
Above-mentioned motor 3 is motor of inner-rotor type, the stator 40 that has rotor 30 and be disposed at the radial outside of this rotor 30 across air gap G.Be fixed with axle 12 at rotor 30.
At above-mentioned seal container 1 suction pipe 11 that sucks refrigerant gas is installed, is connected with gas receiver 10 at this suction pipe 11.That is, above-mentioned compression unit 2 sucks refrigerant gas from above-mentioned gas receiver 10 through above-mentioned suction pipe 11.
Through controlling, thereby obtain this refrigerant gas to constituting with this compressor as not shown condenser, expansion mechanism, the vaporizer of air conditioner of an example of refrigeration system.
The refrigerant gas of the HTHP after in above-mentioned compression unit 2, being compressed is discharged to outside the above-mentioned compression unit 2 and is full of the inside of above-mentioned seal container 1; And; Through the said stator 40 of above-mentioned motor 3 and the air gap G between the above-mentioned rotor 30 etc., be discharged to the outside of seal container 1 from discharge tube 13.In the store oil portion 9 of the bottom of seal container 1, store lubricant oil is arranged.
As shown in Figures 2 and 3, above-mentioned rotor 30 has rotor iron core 31 and embeds this rotor iron core 31 vertically and along a plurality of (being 6 in this mode of execution) magnet 32 of circumferential array.Rotor iron core 31 for example is made up of range upon range of electromagnetic steel plate.
End face that leans on compression unit 2 sides at above-mentioned rotor iron core 31 is provided with the 1st balancer weight 81, is provided with the 2nd balancer weight 82 at another end face of rotor iron core 31.The shape of balancer weight 81,82 for example is circle, horse shoe shaped or U word shape.In addition, also can not shown end plate be installed, balancer weight 81,82 be set at this end plate at the end face of rotor iron core 31.
Said stator 40 has stator iron core 41 that contacts with the internal surface of seal container 1 and the coil 42 that is wound in this stator iron core 41.Stator iron core 41 for example is made up of range upon range of a plurality of electromagnetic steel plates.
Said stator iron core 41 has cylindrical part 45 and a plurality of (being 9 in this mode of execution) tooth portion 46.Tooth portion 46 is outstanding and along circumferential array to radially inner side from the inner peripheral surface of cylindrical part 45.In adjacent tooth portion 46, be formed with slot part 47 between 46.
Above-mentioned coil 42 is the concentrated windings that are wound in each tooth portion 46, rather than crosses over a plurality of above-mentioned tooth portion 46 and reel.Through in coil 42, flowing through electric current, thereby make rotor 30 rotations by electromagnetic force, through rotor 30 rotations, thereby via axle 12 drive compression unit 2.
As shown in Figure 3, above-mentioned compression unit 2 along above-mentioned axle 12 from motor 3 sides successively (according to order from top to bottom) have protecgulum the 50, the 1st cylinder 121, end plate member the 70, the 2nd cylinder 221, bonnet 60.
Above-mentioned protecgulum 50 and above-mentioned end plate member 70 are installed on the opening end up and down of above-mentioned the 1st cylinder 121 respectively.Above-mentioned end plate member 70 and above-mentioned bonnet 60 are installed on the opening end up and down of above-mentioned the 2nd cylinder 221 respectively.
Form the 1st cylinder chamber 122 through above-mentioned the 1st cylinder 121, above-mentioned protecgulum 50 and above-mentioned end plate member 70.Form the 2nd cylinder chamber 222 through above-mentioned the 2nd cylinder 221, above-mentioned bonnet 60 and above-mentioned end plate member 70.
The boss part 52 that above-mentioned protecgulum 50 has the main part 51 of ring-type and is located at interior all sides of this main part 51.Run through for above-mentioned 12 and be inserted in above-mentioned boss part 52.Be provided with the exhaust port 51a that is communicated with above-mentioned the 1st cylinder chamber 122 in aforementioned body portion 51.
To be positioned at the mode of the opposition side of above-mentioned the 1st cylinder 121 with respect to aforementioned body portion 51, expulsion valve 131 is installed in aforementioned body portion 51.This expulsion valve 131 for example is a leaf valve, and above-mentioned exhaust port 51a is opened and closed.
In aforementioned body portion 51,, the premuffler 140 of flat inboard is installed with the mode that covers above-mentioned expulsion valve 131 at the opposition side of above-mentioned the 1st cylinder 121.Above-mentioned boss part 52 runs through the premuffler 140 that is inserted in above-mentioned inboard.
Premuffler 140 through above-mentioned inboard forms the 1st anechoic room 142 with above-mentioned protecgulum 50.Above-mentioned the 1st anechoic room 142 is communicated with via above-mentioned exhaust port 51a with above-mentioned the 1st cylinder chamber 122.
Above-mentioned bonnet 60 have ring-type main part 61, be located at boss part 62 and the perisporium 63 of being located at the outer circumferential side of aforementioned body portion 51 of interior all sides of this main part 61.Run through for above-mentioned 12 and be inserted in above-mentioned boss part 62.Be provided with the exhaust port 61a that is communicated with above-mentioned the 2nd cylinder chamber 222 in aforementioned body portion 61.
To be positioned at the mode of the opposition side of above-mentioned the 2nd cylinder 221 with respect to aforementioned body portion 61, in aforementioned body portion 61 (not shown) expulsion valve is installed, this expulsion valve opens and closes above-mentioned exhaust port 61a.
In aforementioned body portion 61,, flat rear muffler 240 is installed with the mode that covers above-mentioned expulsion valve at the opposition side of above-mentioned the 2nd cylinder 221.Above-mentioned boss part 62 runs through and is inserted in above-mentioned rear muffler 240.
Form the 2nd anechoic room 242 through above-mentioned rear muffler 240 and above-mentioned bonnet 60.Above-mentioned the 2nd anechoic room 242 is communicated with via above-mentioned exhaust port 61a with above-mentioned the 2nd cylinder chamber 222.
Premuffler 140 in above-mentioned inboard at the opposition side of above-mentioned protecgulum 50, is equipped with the premuffler 340 in the outside of cup-shaped with the mode that covers premuffler 140.Form the 3rd anechoic room 342 through the premuffler 140 of above-mentioned inboard and the premuffler 340 in the above-mentioned outside.
Above-mentioned the 1st anechoic room 142 is communicated with through (not shown) hole portion that the premuffler 140 in above-mentioned inboard forms with above-mentioned the 3rd anechoic room 342.
Above-mentioned the 2nd anechoic room 242 and above-mentioned the 3rd anechoic room 342 are communicated with through (not shown) hole portion that forms at above-mentioned bonnet 60, above-mentioned the 2nd cylinder 221, above-mentioned end plate member 70, above-mentioned the 1st cylinder 121 and above-mentioned protecgulum 50.
Above-mentioned the 3rd anechoic room 342 is communicated with through the 340a of hole portion that the premuffler 340 in the above-mentioned outside forms with the outside of the premuffler 340 in the above-mentioned outside.Say that at length the internal surface of the 340a of this hole portion is made up of the outer circumferential face of the boss part 52 of the internal surface of the grooving of the premuffler 340 in the outside and protecgulum 50.
Each parts that constitutes above-mentioned compression unit 2 are fixed by one through a plurality of bolts.The one distolateral boss part 52 of protecgulum 50 and the boss part 62 of bonnet 60 of being supported on of axle 12, axle 12 becomes cantilevered construction.
Be provided with the 1st cam pin 126 that is configured in above-mentioned the 1st cylinder chamber 122 at above-mentioned axle 12.In 126 embeddings of the 1st cam pin the 1st roller 127 is arranged.The 1st roller 127 is configured to can be along the internal surface of above-mentioned the 1st cylinder chamber 122 and around the central axis revolution of above-mentioned the 1st cylinder chamber 122, utilize the revolution motion of the 1st roller 127 to carry out compression.
Be provided with the 2nd cam pin 226 that is configured in above-mentioned the 2nd cylinder chamber 222 at above-mentioned axle 12.In 226 embeddings of the 2nd cam pin the 2nd roller 227 is arranged.The 2nd roller 227 is configured to can be along the internal surface of above-mentioned the 2nd cylinder chamber 222 and around the central axis revolution of above-mentioned the 2nd cylinder chamber 222, utilize the revolution motion of the 2nd roller 227 to carry out compression.
Above-mentioned the 1st cam pin 126 and above-mentioned the 2nd cam pin 226 are positioned at stagger 180 ° position of spin axis with respect to above-mentioned axle 12.
The compression of above-mentioned compression unit 2 then, is described.
At first; In the compression of above-mentioned the 1st cylinder chamber 122; Above-mentioned the 1st cam pin 126 is with the 12 eccentric rotations of above-mentioned axle, be embedded in above-mentioned the 1st cam pin 126 above-mentioned the 1st roller 127 so that the tangent mode of inner peripheral surface of the outer circumferential face of the 1st roller 127 and above-mentioned the 1st cylinder chamber 122 revolve round the sun.
So, from an above-mentioned suction pipe 11 low pressure refrigerant gas is drawn into above-mentioned the 1st cylinder chamber 122, in above-mentioned the 1st cylinder chamber 122, compress and after becoming high pressure, discharge higher pressure refrigerant gas from the exhaust port 51a of above-mentioned protecgulum 50.
Then, the refrigerant gas of discharging from above-mentioned exhaust port 51a is via above-mentioned the 1st anechoic room 142 and above-mentioned the 3rd anechoic room 342, is discharged to the outside of the premuffler 340 in the outside from the exhaust port 340a of the premuffler 340 in the outside.
On the other hand, the compression of above-mentioned the 2nd cylinder chamber 222 is identical with the compression of above-mentioned the 1st cylinder chamber 122.Promptly; From another above-mentioned suction pipe 11 low pressure refrigerant gas is drawn into above-mentioned the 2nd cylinder chamber 222; In above-mentioned the 2nd cylinder chamber 222, utilize the revolution motion of above-mentioned the 2nd roller 227 that refrigerant gas is compressed; Make this higher pressure refrigerant gas via above-mentioned the 2nd anechoic room 242 and above-mentioned the 3rd anechoic room 342, be discharged to the outside of the premuffler 340 in the outside from the exhaust port 340a of the premuffler 340 in the outside.
That is, the refrigerant gas after in above-mentioned compression unit 2, being compressed is discharged to outside the compression unit 2 from the exhaust port 340a with rotor iron core 31 opposed sides that is located at compression unit 2.In addition, the compression of the compression of the 1st cylinder chamber 122 and the 2nd cylinder chamber 222 is in 180 ° the phase place that staggers.
Like Fig. 3 and shown in Figure 4, the discharge volume CR of the axial thickness T of above-mentioned rotor iron core 31 and above-mentioned compression unit 2 satisfies the relation of T/CR≤2.5.The discharge volume CR of compression unit 2 is meant the discharge volume of the 2nd cylinder chamber 222 of the 1st cylinder chamber 122 and the 2nd cylinder 221 of the 1st cylinder 121.
That is, in this compressor, can reduce compressor size through the thickness that reduces rotor iron core 31, and, can increase compressed capability through the discharge volume that increases compression unit 2.Like this, to become size little and have a compressor of big compressed capability for this compressor.
As shown in Figure 4, the part that is positioned near a side of axle 12 of establishing in the inner edge of opening side of exhaust port 340a of premuffler 340 in the above-mentioned outside is radially inner side part P1.In the plane that comprises the radially inner side part P1 and the axis of axle 12, utilize straight line L to connect the periphery ora terminalis P2 near radially inner side part P1 of radially inner side part P1 and above-mentioned rotor iron core 31.At this moment, be configured to, when rotor 30 rotations, do not intersect with straight line L in the 1st balancer weight 81 of the end face setting of leaning on compression unit 2 sides of rotor iron core 31.
Therefore, when air gap G flowed, the 1st balancer weight 81 can not hinder flowing of refrigerant gas to the refrigerant gas in compression unit 2 from exhaust port 340a.Thus, the flow velocity of refrigerant gas can not increase, and suppresses the oil of store oil portion 9 (with reference to Fig. 1) and swarms, and can reduce oiling.
Here, test as follows: change the height H of above-mentioned the 1st balancer weight 81, when obtaining the 1st balancer weight 81 and intersecting and the rate that oils when not intersecting with straight line L with straight line L.Fig. 5 illustrates this result of experiment.Transverse axis illustrates the height [mm] of the 1st balancer weight 81, and the longitudinal axis illustrates the rate of oiling [wt%].
As shown in Figure 5, the gradient of the 2nd diagram line L2 the when gradient of the 1st diagram line L1 the when height of balancer weight 81 is 3.5mm, 4mm, 5mm is 6mm, 7mm, 8mm less than the height of balancer weight 81.
As its reason, when the height of balancer weight 81 was 3.5mm, 4mm, 5mm, balancer weight 81 was not intersected with straight line L, so the refrigerant gas of discharging from exhaust port 340a does not interfere with balancer weight 81.That is, the major part that oils of this moment is that stirring owing to balancer weight 81 causes.Therefore, the gradient of the 1st diagram line L1 is little.
On the other hand, when the height of balancer weight 81 was 6mm, 7mm, 8mm, balancer weight 81 was intersected with straight line L, so the refrigerant gas and the balancer weight 81 of discharging from exhaust port 340a interfere.That is, the major part that oils of this moment is because the stirring of balancer weight 81 and balancer weight 81 and refrigerant gas interfere causes.Therefore, the gradient of the 2nd diagram line L2 is big.
In a word, when the height of balancer weight 81 was 5.8mm, balancer weight 81 was joined with straight line L, and balancer weight 81 beginnings and refrigerant gas interfere.When being 5.8mm with the height of balancer weight 81 is the boundary, and when greater than 5.8mm, the increase degree of the rate that oils rises.The height 5.8mm of balancer weight 81 becomes the graded point C of the 1st diagram line L1 and the 2nd diagram line L2.
Compressor according to said structure; The discharge volume CR of the axial thickness T of above-mentioned rotor iron core 31 and above-mentioned compression unit 2 satisfies the relation of T/CR≤2.5; The 1st balancer weight 81 is configured to when rotor 30 rotations, not intersect with straight line L; So, little and have in the compressor of big compressed capability in size, can reduce oiling.
And above-mentioned compression unit 2 is the two cylinders with the 1st cylinder 121 and the 2nd cylinder 221, so, can further increase the discharge volume of compression unit 2, further increase compressed capability.
In addition, the utility model is not limited to above-mentioned mode of execution.For example, as compression unit, except rotary type, can also use Scrawl and Reciprocatory.
And, in the above-described embodiment, the compression unit of two cylinders is illustrated, still, the utility model can also be applied to the compression unit of single cylinder.Particularly, the compression unit of single cylinder has protecgulum, cylinder, bonnet, premuffler.
Label declaration
1: seal container; 2: compression unit; 3: motor; 12: axle; 30: rotor; 31: rotor iron core; 32: magnet; 40: stator; 41: stator iron core; 42: coil; 46: tooth portion; 50: protecgulum; 60: bonnet; 81: the 1 balancer weights; 82: the 2 balancer weights; 121: the 1 cylinders; 122: the 1 cylinder chamber; 140: inboard premuffler; 221: the 2 cylinders; 222: the 2 cylinder chamber; 240: rear muffler; 340: the premuffler in the outside; 340a: exhaust port; G: air gap; T: (rotor iron core) thickness; P1: (exhaust port) radially inner side part; P2: (rotor iron core) periphery ora terminalis; L: straight line.
Claims (2)
1. a compressor is characterized in that, this compressor has:
Seal container (1);
Compression unit (2), it is configured in the above-mentioned seal container (1); And
Motor (3), it is configured in the above-mentioned seal container (1), and drives above-mentioned compression unit (2) via axle (12),
The stator (40) of above-mentioned motor (3) is disposed at the radial outside of the rotor (30) of above-mentioned motor (3) across air gap (G),
The coil (42) of said stator (40) is wound in the stator iron core (41) of said stator (40),
Above-mentioned coil (42) is the concentrated winding that is wound in each tooth portion (46), rather than a plurality of tooth portions (46) of crossing over said stator iron core (41) reel,
The axial thickness (T) of the rotor iron core (31) of above-mentioned rotor (30) satisfies the relation of T/CR≤2.5 with the discharge volume (CR) of above-mentioned compression unit (2),
Above-mentioned compression unit (2) has exhaust port (340a) with the opposed side of above-mentioned rotor iron core (31), and the refrigerant gas after this exhaust port (340a) will be compressed in above-mentioned compression unit (2) is discharged to outside the above-mentioned compression unit (2),
Radially inner side in the inner edge of above-mentioned exhaust port (340a) part (P1) is positioned at the side near above-mentioned axle (12); In the plane of the axis that comprises said radially inner side part (P1) and above-mentioned axle (12); When the periphery ora terminalis (P2) of the approaching above-mentioned radially inner side part (P1) of utilizing straight line (L) above-mentioned radially inner side part of connection (P1) and above-mentioned rotor iron core (31)
The balancer weight (81) that is provided with at the end face that leans on above-mentioned compression unit (2) side of above-mentioned rotor iron core (31) is configured to, and when above-mentioned rotor (30) rotates, does not intersect with above-mentioned straight line (L).
2. compressor according to claim 1 is characterized in that,
Above-mentioned compression unit (2) has:
The 1st cylinder (121), it has the 1st cylinder chamber (122); And
The 2nd cylinder (221), it has the 2nd cylinder chamber (222).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2012200277608U CN202451425U (en) | 2012-01-20 | 2012-01-20 | Compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2012200277608U CN202451425U (en) | 2012-01-20 | 2012-01-20 | Compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN202451425U true CN202451425U (en) | 2012-09-26 |
Family
ID=46867292
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2012200277608U Expired - Fee Related CN202451425U (en) | 2012-01-20 | 2012-01-20 | Compressor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN202451425U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113738645A (en) * | 2020-05-29 | 2021-12-03 | 广东美芝精密制造有限公司 | Compressor and air conditioning system |
-
2012
- 2012-01-20 CN CN2012200277608U patent/CN202451425U/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113738645A (en) * | 2020-05-29 | 2021-12-03 | 广东美芝精密制造有限公司 | Compressor and air conditioning system |
| CN113738645B (en) * | 2020-05-29 | 2023-03-14 | 广东美芝精密制造有限公司 | Compressor and air conditioning system |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20120926 Termination date: 20200120 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |